TWO-SPEED TRANSMISSION FOR AN ELECTRIC DRIVE SYSTEM, AND DRIVE SYSTEM INCLUDING SUCH A TWO-SPEED TRANSMISSION

Abstract

A compact and fast-shifting two-speed transmission for an electric drive system, such as an electric vehicle, has two synchronized dog clutches. A sliding sleeve for engaging a first and second gear is actuatable using a single actuator. A substantially load-interruption-free shifting is realized via a friction engagement in the synchronization. A drive system having such a two-speed transmission is capable of achieving at least substantially load-interruption-free shifting.

Claims

1. A transmission for an electric drive system for a vehicle, including: a housing an input shaft supported in the housing to be rotatable about a rotational axis an output shaft supported in the housing to be rotatable about the rotational axis a first planetary transmission and a second planetary transmission disposed adjacent to each other coaxially with the rotational axis and having different gear ratios with respect to each other, wherein the first planetary transmission and the second planetary transmission include a common planetary carrier supported in the housing to be rotatable about the rotational axis and connected to the output shaft the first planetary transmission includes a first ring gear supported in the housing to be rotatable around the rotational axis, and the second planetary transmission includes a second ring gear supported in the housing to be rotatable about the rotational axis, a locking device configured to selectively lock the first ring gear or the second ring gear to the housing so that, when the first ring gear is locked to the housing, a torque is transmissible from the input shaft to the output shaft via the first planetary transmission at a first gear ratio and, when the second ring gear is locked to the housing, a torque is transmissible from the input shaft to the output shaft via the second planetary transmission at a second gear ratio, wherein: the locking device includes: a sliding sleeve disposed in the housing to be non-rotatable relative to the housing while being axially movable along the rotational axis, the sliding sleeve having an internal gearing, a first synchronizer body rigidly connected to the first ring gear or formed integrally therewith, the first synchronizer body having an external gearing configured to be bringable into engagement with the internal gearing of the sliding sleeve by moving the sliding sleeve along the rotational axis into a first position, a second synchronizer body rigidly connected to the second ring gear or formed integrally therewith, the second synchronizer body having an external gearing configured to be bringable into engagement with the internal gearing of the sliding sleeve by moving the sliding sleeve along the rotational axis into a second position, and a displacing device having an actuator configured to displace the sliding sleeve along the rotational axis between the first position and the second position, the first synchronizer body has a first friction region on a side facing the second synchronizer body and the second synchronizer body has a second friction region on a side facing the first synchronizer body a first synchronizer ring has an external gearing configured to be bringable into engagement with the internal gearing of the sliding sleeve by actuating the actuator to move the sliding sleeve along the rotational axis, the first synchronizer ring has a third friction region configured to abut against the first friction region of the first synchronizer body a second synchronizer ring has an external gearing configured to be bringable into engagement with the internal gearing of the sliding sleeve by actuating the actuator to move the sliding sleeve along the rotational axis, the second synchronizer ring has a fourth friction region (44), which is configured to abut against the second friction region of the second synchronizer body the locking device is configured to actuate the actuator to move the sliding sleeve along the rotational axis using into a synchronization position, in which the internal gearing of the sliding sleeve is not in engagement with the external gearings of the first and second synchronizer bodies while simultaneously the internal gearing of the sliding sleeve is at least partially in engagement with the external gearings of both of the first and second synchronizer rings, and force is exerted by the sliding sleeve in the direction of the rotation axis onto one of the first or second synchronizer rings such that the corresponding first or second synchronizer body is brakeable by the friction engagement with said one of the first or second synchronizer rings and the fourth friction region of the second synchronizer ring and the first friction region of the second synchronizer body are dimensioned such that both have a torque capacity sufficient to transmit a torque to the output shaft in the synchronization position while the sliding sleeve moves from the first position into the second position.

2. The transmission according to claim 1, wherein the locking device is further configured to actuate the actuator to bring the sliding sleeve into a neutral position, in which the internal gearing of the sliding sleeve is not in engagement with the external gearings of the first and second synchronizer bodies while being simultaneously in engagement with the external gearing of only one of the first or second synchronizer rings.

3. The transmission according to claim 1, wherein the locking device is configured to actuate the actuator to move the sliding sleeve along the rotational axis into a pre-synchronization position, in which the internal gearing of the sliding sleeve is not in engagement with the external gearings of the first or second synchronizer bodies while simultaneously the internal gearing of the sliding sleeve is in engagement with the external gearing of only one of the first or second synchronizer rings and while simultaneously the sliding sleeve brings a locking strut which is not rotatable relative to the sliding sleeve into axial abutment against the other of the first or second synchronizer rings and presses the other of the first or second synchronizer rings against the corresponding first or second synchronizer body, such that the other of the first or second synchronizer ring is rotated relative to the sliding sleeve into a lock position, in which the internal gearing of the sliding sleeve and the external gearing of the other first or second synchronizer ring are rotated relative to each other.

4. (canceled)

5. The transmission according to claim 1 wherein the internal gearing of the sliding sleeve has a width in the direction of the rotational axis that is greater than a distance between the external gearings of the first and second synchronizer rings in the direction of the rotational axis and that is smaller than a distance between the external gearing of one of the first or second synchronizer bodies and the external gearing of the respective other one of the first or second synchronizer ring in the direction of the rotational axis.

6. The transmission according to claim 1 wherein the internal gearing of the sliding sleeve has a diameter that is greater than the diameter of the internal gearing of a smaller one of the first or second ring gear.

7-8. (canceled)

9. The transmssion according to claim 1, wherein: the displacing device includes: a worm shaft that is drivable by the actuator, a worm gear disposed coaxially with the sliding sleeve and disposed on an outer circumference side of the sliding sleeve such that, as viewed starting from the rotational axis in a radial direction perpendicular to the rotational axis, the sliding sleeve at least partially overlaps the worm gear and is rotatable by the worm shaft about the rotational axis, and a guide pin provided on the sliding sleeve and protruding radially outward therefrom, wherein: a guide groove that receives the guide pin is provided in the worm gear, the guide groove extending at an angle (α) to the circumferential direction so that, in response to rotation of the worm gear by an angle (β), the sliding sleeve displaces a distance (x) along the rotational axis, and the actuator is an electric motor.

10. (canceled)

11. The transmission according to claim 1 wherein: the first and second ring gears are supported radially on the planetary gears a first bearing is disposed between the housing and a side of the first ring gear facing away from the second ring gear, a second bearing is disposed between the housing and a side of the second ring gear facing away from the first ring gear, and a third bearing provides axial support between the first and second ring gears.

12. (canceled)

13. The transmission according to claim 1 wherein, in the synchronization position, the internal gearing of the sliding sleeve is partially in engagement with the external gearing of one of the first or second synchronizer rings such that tooth-heads and tooth-troughs of the internal gearing of the sliding sleeve and of the external gearing of said one of the first or second synchronizer ring are rotated by an angle relative to one another to apply an axial force to said one of the first or second synchronizer ring, and the tooth-heads and tooth-troughs of the internal gearing are simultaneously in engagement with the external gearing of the other one of the first or second synchronizer ring such that the tooth-heads and tooth-troughs of the internal gearing of the sliding sleeve and of the external gearing of said other one of the first or second synchronizer ring (34) are not rotated relative to each other, so that no axial force is applied to said other one of the first or second synchronizer ring via this tooth engagement.

14. A transmission including a housing and a locking device wherein the locking device includes: a sliding sleeve movably supported in the housing along a movement axis, and having an internal gearing, a central axis of the sliding sleeve is being coaxial with the movement axis, a first synchronizer body disposed coaxially with the sliding sleeve the first synchronizer body having an external gearing configured to be bringable into engagement with the internal gearing of the sliding sleeve by moving the sliding sleeve along the movement axis, and having a first friction region a second synchronizer body disposed coaxially with the sliding sleeve the second synchronizer body having an external gearing configured to be bringable into engagement with the internal gearing by moving the sliding sleeve along the movement axis, and having a second friction region a first synchronizer ring having an external gearing configured to be bringable into engagement with the internal gearing (2-0) of the sliding sleeve by moving the sliding sleeve along the movement axis, and having a third friction region configured to abut against the first friction region of the first synchronizer body and a second synchronizer ring having an external gearing configured to be bringable into engagement with the internal gearing of the sliding sleeve by moving the sliding sleeve along the movement axis, and having a fourth friction region configured to abut against the second friction region of the second synchronizer body, wherein the locking device is configured such that: the sliding sleeve is configured to be bringable into a neutral position, in which the internal gearing of the sliding sleeve is not in engagement with the external gearing of the first synchronizer body and is not in engagement with the external gearing of the second synchronizer bodywhile simultaneously being in engagement with the external gearing of only one of the first or second synchronizer rings, and in a movement along the rotational axis, the sliding sleeve is configured to be bringable into a synchronization position, in which the internal gearing of the sliding sleeve is not in engagement with the external gearings of the first or second synchronizer bodies and simultaneously the internal gearing of the sliding sleeve is partially in engagement with the external gearing of one of the first or second synchronizer rings such that tooth-heads and tooth-troughs of the internal gearing of the sliding sleeve and of the external gearing of said one of the first or second synchronizer ring are rotated by an angle relative to each other to apply an axial force to said one of the first or second synchronizer rings such that the corresponding synchronizer body is synchonizable with said one of the first or second synchronizer rings via frictional engagement, while also being in engagement with the external gearing of the other one of the first or second synchronizer rings such that the tooth-heads and tooth-troughs of the internal gearing of the sliding sleeve and of the external gearing of the other one of the first or second synchronizer rings are not rotated relative to each other, so that no axial force is applied to the other one of the first or second synchronizer rings via this tooth engagement.

15-19. (canceled)

20. The transmission according to claim 14, wherein the internal gearing of the sliding sleeve has a width that is between 1% and 10% smaller than a distance between the external gearing of said one of the first or second synchronizer bodies and the external gearing of the respective opposing synchronizer ring .

21. (canceled)

22. An electric drive system for a vehicle, including: an electric drive machine, a transmission according to claim 1, wherein the drive system is configured such that, in a shifting process in which the sliding sleeve is moved from the first position into the second position, a torque is transmissible between the fourth friction region and the second friction region in the synchronization position via the abutment of the fourth friction region of the second synchronizer ring against the second friction region of the second synchronizer body said torque being greater than 30% of a maximum rotational speed torque of the electric drive machine that is maximally deliverable by the electric drive machine at maximum rotational speed .

23. The electric drive system according to claim 22, wherein the locking device is configured such that: in the shifting process, in which the sliding sleeve is moved from the first position into the second position, the said torque transmitted in the synchronization position via the fourth and second friction regions remains substantially constant, or in the shifting process, in which the sliding sleeve is moved from the first position into the second position, the said torque transmitted in the synchronization position via the fourth and second friction regions increases with decreases of the rotational speed of the electric drive machine such that power delivered at the output shaft during the synchronization remains constant, and/or the power delivered at the output shaft during the synchronization corresponds to the power that is output at the output shaft immediately before the moving of the sliding sleeve from the first position into the second position.

24. The electric drive system according to claim 22, wherein the locking device is configured such that the shifting process, in which the sliding sleeve is moved from the first position into the second position, is triggered at a shifting rotational speed that is set such that, at a substantially constant rotational speed of the output shaft during the shifting process, the rotational speed of the electric drive machine after the shifting process remains in a constant power range of the electronic drive machine.

25. The electric drive system according to claim 24, wherein the locking device is configured such that the shifting process, in which the sliding sleeve is moved from the first position into the second position, is triggered at the maximum rotational speed of the electric drive machine .

26. The electric drive system according to claim 22, wherein the locking device is configured such that: said torque, which is transmitted in the synchronization position via the fourth and second friction regions, corresponds to the maximum rotational speed torque, and/or remains constant during the synchronization, so thatpower delivered at the output shaft immediately before the shifting process continuously drops only slowly with decreasing of the rotational speed of the electric drive machine during the shifting process, or said torque, which is transmitted in the synchronization position via the fourth and second friction regions, is at least temporarily lower or higher than the maximum rotational speed torque, and/or decreases or increases during the synchronization, so that power delivered at the output shaft immediately before the shifting process remains constant during the synchronization, or changes only continuously and not in an erratic manner.

27. An electric drive system according to claim 22, wherein the drive system is configured such that, while the sliding sleeve is moving from the first position into the second position, the torque that is available at the output shaft does not change direction, so that propulsion is continuously deliverable.

28. An electric drive system according to claim 22, wherein the drive system is configured such that, while the sliding sleeve is moving from the first position into the second position, the electric drive machine is electrically braked in the synchronization position in addition to the braking by the fourth and second friction regions .

29. An electric drive system according to claim 22, wherein the locking device is configured such that in the shifting process, in which the sliding sleeve is moved from the first position into the second position, a torque of the second ring gear is supported in the synchronization position by the fourth and second friction regions and said torque is transmitted to the output shaft for reducing or preventing a load interruption.

30. (canceled)

31. The transmission according to claim 2, wherein, in the synchronization position, the internal gearing of the sliding sleeve is partially in engagement with the external gearing of one of the first or second synchronizer rings such that tooth-heads and tooth-troughs of the internal gearing of the sliding sleeve and of the external gearing of said one of the first or second synchronizer ring are rotated by an angle relative to one another to apply an axial force to said one of the first or second synchronizer ring, and the tooth-heads and tooth-troughs of the internal gearing are simultaneously in engagement with the external gearing of the other one of the first or second synchronizer ring such that the tooth-heads and tooth-troughs of the internal gearing of the sliding sleeve and of the external gearing of said other one of the first or second synchronizer ring are not rotated relative to each other, so that no axial force is applied to said other one of the first or second synchronizer ring via this tooth engagement.

32. The transmission according to claim 14, wherein the internal gearing of the sliding sleeve has a width in the direction of the rotational axis that is greater than a distance between the external gearings of the first and second synchronizer rings in the direction of the rotational axis and that is smaller than a distance between the external gearing of one of the first or second synchronizer bodies and the external gearing of the respective other one of the first or second synchronizer ring in the direction of the rotational axis.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0052] The invention is explained in the following by way of example and with further details with the aid of schematic drawings. In the Figures:

[0053] FIG. 1 shows a schematic representation of an electric drive system having a transmission according to a first embodiment.

[0054] FIG. 2 shows a schematic diagram of an electric drive system having a transmission according to a second embodiment.

[0055] FIG. 3 shows a detail section of a first cross-sectional view of the transmission according to the second embodiment in a neutral position.

[0056] FIG. 4 shows a detailed representation of a displacing device of the transmission according to the second embodiment in the neutral position.

[0057] FIG. 5 shows a detail section of the first cross-sectional view of the transmission according to the second embodiment in which the first gear is engaged.

[0058] FIG. 6 shows a detail representation of the displacing device of the transmission according to the second embodiment in a state in which the first gear is engaged.

[0059] FIG. 7 shows a detail section of a second cross-sectional view of the transmission according to the second embodiment in a pre-synchronization position for the second gear.

[0060] FIG. 8 shows a detail section of the first cross-sectional view of the transmission according to the second embodiment in the synchronization position for the second gear.

[0061] FIG. 9 shows a detail representation of the displacing device of the transmission according to the second embodiment in the synchronization position for the second gear.

[0062] FIG. 10 shows a detail section of the second cross-sectional view of the transmission according to the second embodiment in the synchronization position for the second gear.

[0063] FIG. 11 shows a detail section of the first cross-sectional view of a transmission according to the second embodiment, in which the second gear is engaged.

[0064] FIG. 12 shows a detail representation of the displacing device of the transmission according to the second embodiment in a state in which the second gear is engaged.

[0065] FIG. 13 shows a detail section of the second cross-sectional view of the transmission according to the second embodiment in a pre-synchronization position for the first gear.

[0066] FIG. 14 shows various possible shifting processes in an idealized characteristic curve of an electric drive machine having exemplary switching processes for the shifting from a first gear into a second gear.

DETAILED DESCRIPTION OF THE INVENTION

[0067] A schematic diagram of an electric drive system having an electric drive machine (E-motor) EM and a two-speed transmission according to a first embodiment having two different sized sun gears 1′ and 1, which are provided on a common input shaft E that serves as a drive for the sun gears, is shown in FIG. 1. The input shaft E is disposed coaxially with a rotational axis X and is supported in the housing G. In the housing, two ring gears 14, 16 are further supported coaxially with the rotational axis and to be rotatable about it. Furthermore, a locking device 2, which is provided for braking each one of the differently sized ring gears 14, 16, is provided. Furthermore, first planetary gears 6′ and second planetary gears 6, which are supported on a common bridge (planet carrier) S to be rotatable about it, are provided. The bridge S is in turn supported such that it rotates about the rotational axis. One end of the bridge S is configured to be coaxial with the rotational axis X, and serves as output shaft A or an output. A plurality of such planetary gears 6′ and 6 are preferably distributed around the circumference as planetary gear sets. The planetary gears 6′ and 6 mesh with the ring gears 14 and 16 and the sun gears 1′ and 1. A reverse transmission of the simplest design is respectively formed by a group that is respectively made of a sun gear, a planet set supported on a bridge, and a ring gear. In total, two planetary transmissions 10, 12 (in particular, reverse transmissions of the simplest design) disposed adjacent to each other are provided which, due to the different numbers of teeth/diameter of the individual gears, provide two gear ratios between input shaft E and output shaft A, which gear ratios are different from each other. Each of the two reverse transmissions 10, 12 can then transmit a torque from the input E to the output A only when the particular ring gear for the supporting of the torque is locked (stopped) with respect to the housing G by the locking device 2. The first planetary transmission 10 (input shaft E, sun 1′, planetary gear 6′, bridge S, ring gear 14) can thus transmit a torque only when the first ring gear 14 is held locked using the locking device 2. The second planetary transmission 12 can transmit torque in a corresponding manner by locking of the second ring gear 16.

[0068] FIG. 2 shows a schematic diagram of an electric drive system having an electric drive machine (E-motor) EM and a two-speed transmission according to a second embodiment. In contrast to the transmission shown in FIG. 1, only a single sun gear 1 that is fixedly disposed on an input shaft E is provided; and per planetary gear set, the planetary gears 6 belonging to the first planetary transmission are respectively rigidly connected to the planetary gears 6′ belonging to the second planetary transmission. These connected planetary gears are supported together on the bridge to be rotatable about it. In particular, the planetary gears 6′ and 6, which are connected to each other such that they rotate together, can also be configured as a one-part stepped planetary gear. The different gear ratios of the first and second gears also arise here exactly as in FIG. 1 by locking one of the ring gears 14 and 16 using the locking device 2. For both transmissions, the output is the common bridge S, which also, as usual with reverse transmissions, transmits the highest torque.

[0069] The following applies to the transmission according to FIG. 1;

[0070] The gear ratio i.sub.1st gear = i.sub.1′S of the first gear (locking of the first ring gear 14) arises from the static gear ratio i.sub.1′ 14 of the first reverse transmission 10 with [0071] i.sub.1′ 14 = d.sub.H14/d.sub.1′ with [0072] i.sub.1′S = 1 - i.sub.1′ 14 wherein [0073] d.sub.H14 = diameter of the first ring gear 14 [0074] d.sub.1′= diameter of the sun gear 1′

[0075] The gear ratio i.sub.2nd .sub.gear= i.sub.1S of the second gear (locking of the second ring gear 16) arises from static gear ratio i.sub.1 16 of the second reverse transmission with [0076] i.sub.1 16 = d.sub.H16/d.sub.1 with [0077] i.sub.1S = 1-i.sub.1-16 [0078] wherein [0079] d.sub.H16 = diameter of the second ring gear 16 [0080] d.sub.1= diameter of the sun 1

[0081] The following applies to the transmission according to FIG. 2;

[0082] The gear ratio i.sub.1st .sub.gear = i.sub.1S of the first gear (locking of the first ring gear 14) arises from static gear ratio i.sub.1 14 of the first reverse transmission with [0083] i.sub.1 14 = (d.sub.H14/d.sub.6′)* (d.sub.6/d.sub.1) with [0084] i.sub.1S = 1 - i.sub.1 14 wherein [0085] d.sub.H14 = diameter of the first ring gear 14 [0086] d = diameter of the sun 1 [0087] d.sub.6′ = diameter of the smaller planetary gear 6′ [0088] d.sub.6 = diameter of the larger planetary gear 6

[0089] The gear ratio i.sub.2nd .sub.gear = i.sub.1S of the second gear (locking of the second ring gear 16) arises from static gear ratio i.sub.1 .sub.16 of the second reverse transmission with [0090] i.sub.1 16 = d.sub.H16/d.sub.1 with [0091] i.sub.1S = 1 - i.sub.1 16 [0092] wherein [0093] d.sub.H16 = diameter of the second ring gear 16 [0094] d.sub.1= diameter of the sun 1

[0095] The difference of the two transmissions is in the achievable gear ratio range. By way of example, for the gear ratio range i.sub.2nd gear ≈ +2 and i.sub.1stgear ≈ +5, the transmission from FIG. 1 is used and, for the gear ratio range i.sub.2nd .sub.gear ≈ +8 and i.sub.1st gear ≈ +15, the transmission from FIG. 2 is used.

[0096] For the gear ratios of FIG. 1, the gear ratios i.sub.1S result from the two simple reverse transmissions i.sub.1′ 14 und i.sub.1 16.

[0097] Starting from the two above-mentioned embodiments, the locking device 2 common to the two transmissions is described based on the second embodiment from FIG. 2 with reference to the further Figures. Here it is to be noted that FIGS. 1 and 2 respectively are only schematic diagrams from which the actual arrangement of the individual components, their dimensions, etc. do not necessarily follow or do not follow in all aspects. FIGS. 3 to 10 are more precise in this respect and also, however, represent schematic diagrams of a possible actual design, but not true to scale. In particular, the Figures are in part depicted at different magnifications among one another and possibly also not completely rigorously with respect to one another.

[0098] If not indicated otherwise, identical reference numbers mean that the same respective component is intended. Not all reference numbers are indicated in all Figures, but rather only those that are particularly relevant. Components not specified in individual Figures, which components have received a reference number in other Figures, are therefore unchanged unless indicated otherwise.

[0099] In addition to the details of the locking device 2, portions of the housing G and portions of the ring gears 14, 16 are shown in FIGS. 3, 5, 8 and 11. The rotational axis X is located below in each and is not depicted.

[0100] Using the locking device 2, the first ring gear 14 or the second ring gear 16 is selectively lockable to the housing G so that, when the first ring gear 14 is locked, a torque is transmissible from the input shaft E to the output shaft A via the first planetary transmission 10 and, when the second ring gear 16 is locked, a torque is transmissible from the input shaft E to the output shaft A via the second planetary transmission 12.

[0101] As shown in the first cross-sectional view of FIG. 3, the locking device 2 is configured as follows: [0102] a cylindrical sliding sleeve 18, which is coaxial with the rotational axis, is provided in the housing G to be non-rotatable relative to the housing G and to be axially movable along the rotational axis X. For this purpose, the sliding sleeve 18 includes a gearing on the external side, and the housing G includes a gearing (for example, spline 19) on the internal side. The sliding sleeve further includes an internal gearing 20.

[0103] A cylindrical first synchronizer body 22 is rigidly connected with the first ring gear 14 (for example, press fitted) or is formed as one-part (integrally) therewith and is provided on an outer circumference of the ring gear. The first synchronizer body 22 has an external gearing 24 configured to be coaxial with the rotational axis, which external gearing 24 is configured such that it is bringable into engagement with the internal gearing 20 of the sliding sleeve 18 by moving the sliding sleeve 18 along the rotational axis X. The diameter of the internal gearing 20 of the sliding sleeve 18 is thus greater than the outer diameter of the smaller first ring 14. A cylindrical second synchronizer body 26 is rigidly connected with the second ring gear 16 (for example, press-fitted) or is formed as one-part (integral) therewith. In particular, the second ring gear 16 is connected on an outer side to a cylindrical connecting component 17 such that they rotate together, if it is not integrally formed together. The connecting component extends axially toward the first synchronizer body 22 with a radially inwardly stepped section; the second synchronizer body 26 is provided on the axial end projection of the radially inwardly stepped section. It is thereby made possible that the second ring gear 16 has a greater diameter than portions of the locking device. Furthermore, this makes it possible that the second ring gear 16 is disposed substantially adjacent to the locking device 2. The radial installation space of the transmission can thus be optimized.

[0104] The second synchronizer body 26 has an external gearing 28 configured to be coaxial with the rotational axis X, which external gearing 28 is configured such that it is bringable into engagement with the internal gearing 20 of the sliding sleeve 18 by moving the sliding sleeve 18 along the rotational axis X. On the side facing the second synchronizer body 26, the first synchronizer body 22 has an axial projection that is formed as friction region 30, which conically tapers toward the second synchronizer body 26. On the side facing the first synchronizer body 22, the second synchronizer body 26 has an axial projection that is formed as friction region 32, which conically tapers toward the first synchronizer body 22. The first and the second synchronizer bodies 22, 26, or the ring gears 14 and 16 onto which they are attached, are supported in a substantially not axially displaceable manner. The friction regions can be formed integrally or as a coating.

[0105] Furthermore, a first synchronizer ring 34, which is disposed to be coaxial with the rotational axis, is provided. The first synchronizer ring 34 has an external gearing 36 that is configured such that it is bringable into engagement with the internal gearing 20 of the sliding sleeve 18 by moving the sliding sleeve 18 along the rotational axis X (radial overlapping). Furthermore, on the side facing the second synchronizer body 26, the first synchronizer ring 34 has a projection region that includes a friction region 38, which conically tapers on the inner-circumference side toward the second synchronizer body 26. The friction region 38 is configured such that, when an axial force is applied to the first synchronizer ring 34 in the direction toward the first synchronizer body 22, the friction region 38 can form a friction engagement with the friction region 30 of the first synchronizer body 22.

[0106] The first synchronizer ring 34 further has at least one radially outwardly protruding pre-synchronization projection on its side of the external gearing 36 that faces the second synchronizer body 26; the pre-synchronization projection is not shown in the first cross-sectional view of FIG. 3, but is configured as is usual for synchronized transmissions. In a corresponding manner, the sliding sleeve 18 has, on its inner circumferential side, a pre-synchronization groove, which also is not shown but is configured as usual. Via the pre-synchronization projection and the pre-synchronization groove, the first synchronizer ring 34 is preferably supported radially in the sliding sleeve independently of the axial position (i.e., at every position) of the sliding sleeve. The pre-synchronization projection and the pre-synchronization groove are further configured such that a relative rotation of the first synchronizer ring 34 with respect to the sliding sleeve 18 by a predetermined angle between a lock position and a released position is possible. A further rotation of the first synchronizer ring 34 with respect to the sliding sleeve 18 is prevented. The released position is defined as a relative rotation position, at which the teeth of the first synchronizer ring 34 are aligned with the teeth of the sliding sleeve 18, i.e., at which the sliding sleeve 18 is freely displaceable from a position, in which the internal gearing 20 is not in engagement with the external gearing 36 of the first synchronizer ring 34, into an engagement position. Conversely, the lock position is defined as a relative rotation position, at which the front ends in the axial direction of the tooth heads of the synchronizer ring 34 are offset in the circumferential direction with respect to the tooth bases of the sliding sleeve; i.e., they are relatively rotated with respect to the aligned position.

[0107] The first synchronizer ring 34 is radially supported in the sliding sleeve in an axially displaceable manner, and, depending on the axial position, is also supported via its conical friction region 38 on the conical friction region 30 of the first synchronizer body 22. A displacement of the first synchronizer ring 34 toward the external gearing 24 of the first synchronizer body 22 causes the contact pressure, with which the friction regions lie against one another, to increase, which also leads to an increased friction between the first synchronizer body 22 and the first synchronizer ring 34. This contact pressure also limits a movement in this direction. An opposing movement of the first synchronizer ring 34 away from the external gearing 24 of the first synchronizer body 22 leads to a reduction of the contact pressure, so that the friction is also reduced. The movement away from the external gearing 24 can be limited, for example, by a locking strut 39, etc., which is not shown in the first cross-sectional view of FIGS. 3, 5, 8 and 11. The first synchronizer ring 34 is therefore movably (in a bounded manner) supported on the first synchronizer body 22.

[0108] Furthermore, a second synchronizer ring 40, which is preferably formed in a symmetrical manner with a respect to a symmetry plane between the first and second synchronizer bodies, which symmetry plane is perpendicular to the rotational axis, is provided, the first synchronizer ring 40 being disposed coaxially with the rotational axis. The second synchronizer ring 40 has an external gearing 42 that is configured such that it is bringable into engagement with the internal gearing 20 of the sliding sleeve 18 by moving the sliding sleeve 18 along the rotational axis X. The second synchronizer ring 40 further has a projection region on the side facing the first synchronizer body 22, which projection region includes a friction region 44 that conically tapers on the inner circumference side toward the first synchronizer body 22. The friction region 44 is configured such that it can form a friction engagement with the friction region 32 of the second synchronizer body 26. The second synchronizer ring 40 as well as the first synchronizer ring 34 have a not-shown pre-synchronization projection that is held in a correspondingly configured pre-synchronization groove, and is relatively rotatable between a lock position and a released position in a manner analogous to the first synchronizer ring 34. The supporting and increasing or reducing of the contact pressure is analogous (but mirror-reversed) to the first synchronizer ring 34.

[0109] The external gearing 24 of the first synchronizer body 22 is preferably substantially symmetric with respect to the external gearing 28 of the second synchronizer body 26, and the external gearing 36 of the first synchronizer ring 34 is preferably substantially symmetric with respect to the external gearing 42 of the second synchronizer ring 40, respectively, with respect to a symmetry plane lying between them.

[0110] Furthermore, a displacing device 46, which is also depicted in particular in more detail in FIG. 4, is provided for displacing the position of the sliding sleeve 18 along the rotational axis X.

[0111] The displacing device 46 includes an electric motor 48 for driving a worm shaft 50. Both are supported in the housing G. Using the worm shaft 50, a worm gear 52 is driven via an external gearing provided on the worm gear. The worm gear 52 is disposed coaxially with the sliding sleeve 18 and is rotatable relative to it about the rotational axis X. The worm gear 52 is provided on the outer circumference side with respect to the sliding sleeve 18, and does not contact it or is at least basically freely rotatable about it. The worm gear 52 is supported in the housing in an axially non-displaceable manner. The worm gear 52 is axially guided between two housing parts and is supported radially, wherein the partition plane (contact surface between the two housing parts) is not depicted, and is freely selectable by the designer within the width b2 of the worm gear.

[0112] The worm gear 52 further includes a plurality of guide grooves 54 that extend in a straight line manner over a predetermined length along the circumferential direction, but are inclined with respect thereto by an angle α. Here the length in the circumferential direction is r*β in radian measure, with β as the rotational angle of the worm gear 52 between the one end position and the other end position, and r as the radius of the worm gear. The guide grooves 54 are formed at least on an inner circumference side or extend completely through the worm gear 52 in their depth direction.

[0113] Furthermore, multiple guide pins 56, which protrude radially outwardly, are provided on the sliding sleeve 18, which guide pins 56 are preferably rigidly provided on the sliding sleeve, for example, by press fitting. Here the guide pins 56 and the guide grooves 54, or the arrangement of the sliding sleeve 18 and the worm gear 52, are configured such that, in the assembled state of the transmission, each of the guide pins 56 is guided in one of the guide grooves 54. As already indicated above, the sliding sleeve 18 is radially supported, in a displaceable manner in the axial direction, in the housing G via an external gearing on the inner side along the gearing 19. The displacing and guiding of the sliding sleeve 18 in the axial direction is achieved using the guide pins 56. These are guided in the guide grooves 54 such that, by rotating the worm gear 52, the position of the sliding sleeve 18 is displaceable in the axial direction. In particular, starting from a desired travel distance X.sub.Total = X.sub.axial1 + X.sub.axial2 of the sliding sleeve 18 (see FIG. 4) and a prescribed inclination α of the guide groove with respect to the circumferential direction, the following angle of rotation β.sub.Total (in radian measure) of the worm gear results:

[00001] $β_{Total} = (x_{axial1} + x_{axial2}) / \tan α * r$

[0114] Here the total travel distance X.sub.Total = .sub.Xaxial1 + X.sub.axial2 corresponds to the distance that the sliding sleeve 18 must travel in the axial direction from a full engagement with the first synchronizer body 22 to a full engagement with the second synchronizer body 26. Using the inclination angle α, the force ratio for applying an axial force using the sliding sleeve to establish the synchronization can be set.

[0115] Furthermore, the sliding sleeve 18 is configured such that it has a width that is greater than the spacing of the external gearings 36, 42 of the synchronizer rings 34, 40 in the axial direction (= there is a position, at which both synchronizer rings are in engagement) and is smaller than the distance in the axial direction (in the synchronization position, the opposing synchronizer body is no longer in engagement) of the external gearings 24, 28 of one of the synchronizer bodies 22, 26 to the respective opposing synchronizer ring 34, 40 (associated with the other synchronizer body).

[0116] The gearings that engage in each other during shifting from the first gear to the second gear, i.e., the external gearings 24, 28 of the synchronizer bodies 22, 26, the external gearings 36, 42 of the synchronizer rings 34, 40, and the internal gearing 20 of the sliding sleeve 18, have the above-described chamfered teeth, in which the axial tooth ends converge to a point or converge to the shape of a triangle.

[0117] Preferably there are additional bearings 58 and 60 for supporting the stepped planets 6, 6′, and a bearing 62 that provides an axial supporting of the ring gears 14 and 16.

[0118] Furthermore, as can be seen from the second cross-sectional views in FIGS. 7, 10 and 13, which are different from the first cross-sectional views in FIGS. 3, 5, 8 and 11, the locking strut 39 is provided, using which a so-called pre-synchronization is achievable for displacing the synchronizer rings 34, 40 into the lock position. The locking strut 39 is disposed in a space that is delimited on the outer circumference side by the sliding sleeve 18, on the inner circumference side by the outer-circumference sides of the friction regions 38, 44 of the synchronizer rings 34, 40, and in the axial direction by the radially outwardly protruding external gearings 36, 42 of the synchronizer rings 34, 40. The locking strut 39 is preloaded, radially outward against a corresponding locking-strut receiving region that is formed on the inner-circumferential side of the sliding sleeve 18, by a spring 39a that is disposed and attached in the circumferential direction inside the sliding sleeve 18. At its ends in the axial direction, the locking strut 39 is truncated on the outer circumference side with respect to a central part, and thus has two oblique abutment surfaces 39b. Centrally radially outside the synchronizer rings 34, 40, the locking-strut receiving region includes a recess and thus has two oblique abutment surfaces 39c corresponding to the abutment surfaces 39b. The oblique abutment surfaces 39c in the locking-strut receiving region are disposed closer to each other in the axial direction than the oblique abutment surfaces 39b of the locking strut 39. The locking strut is thus not insertable into the recess with both abutment surfaces 39b simultaneously.

[0119] Overall, the locking strut 39 having its abutment surfaces 39b, and the locking-strut receiving region having its abutment surfaces 39c, are configured such that at least the following relevant positions can be achieved: the locking strut 39 is disposed parallel to the sliding sleeve 18, and none of the abutment surfaces come into contact with one another (see FIG. 10). In this position, the abutment surfaces 39b of the locking strut 39 are disposed, for example, in front of and behind the abutment surfaces 39c of the sliding sleeve 18 in the axial direction. Or, the locking strut 39 is axially displaced and tilted perpendicularly to the circumferential direction such that one of the abutment surfaces 39b of the locking strut 39 is in engagement with the corresponding abutment surface 39c (see FIGS. 7 and 13). Only in the latter case can an axial force be exerted by the sliding sleeve 18 onto the locking strut 39. In total, preferably at least three locking struts 39 are provided.

[0120] In the following, individual operating states and positions of the transmission are described:

[0121] FIGS. 3 and 4 show a neutral position of the sliding sleeve 18 in which the vehicle is stationary, for example. Even when the motor (the input shaft; drive machine) is rotating, no torque can be transmitted, since the inner gearing 20 of the sliding sleeve 18 is only in engagement with the external gearing 36 of one of the synchronizer rings (here, of the first synchronizer ring 34) and, owing to the lack of an axial force, the first synchronizer ring 34 also is not in friction engagement with the first synchronizer body 22. Even if the sliding sleeve 18 were to be moved toward the first synchronizer body 22, substantially no axial force would be exertable onto the first synchronizer ring 34 via the internal gearing 20 of the sliding sleeve 18 due to the complete tooth engagement with the external gearing 36 of the first synchronizer ring 34. A synchronization would thus not take place. Therefore, to engage the first gear when the vehicle is stationary, the motor must be stopped starting from this neutral position.

[0122] Starting from the neutral position, when the motor and vehicle are stationary, the first gear can be engaged by moving the sliding sleeve 18 using the displacing device 46 by the distance X.sub.axial,.sub.1 toward the first synchronizer body 22 (see FIG. 3). The position of the sliding sleeve, when the first gear is fully engaged, is shown in FIGS. 5 and 6. For full torque transmission, the internal gearing 20 of the sliding (shifting) sleeve 18 is in full tooth engagement with the external gearing 24 of the first synchronizer body 22 in the first-gear position. “Full tooth engagement” means here that the entire width of the external gearing 24 is in engagement with the internal gearing 20. Accordingly, a tooth engagement or contact of the internal gearing 20 of the sliding sleeve 18 with the second synchronizer ring 40 or the second synchronizer body 26 does not exist. As can be seen from FIG. 6, in the first-gear position the guide pin 56 is disposed in one end position of the guide groove.

[0123] For the engaging of the first gear, the sliding sleeve 18 therefore need only travel the short distance X.sub.axial,1, wherein this distance substantially corresponds to the width of the external gearing 24 of the first synchronizer body 22 (actually, the distance corresponds to the width plus the spacing that the internal gearing 20 has to the external gearing 24 of the first synchronizer body 22 in the neutral position).

[0124] If shifting now occurs into the second gear having the lower gear ratio while the motor is rotating and the vehicle is driving, the sliding sleeve 18 is moved by the shifting device 46 starting from the first-gear-position in the direction toward the second synchronizer body 26 in order to release a rotation of the first ring gear 14 and to stop or lock the rotating second ring gear 16. In this movement, the neutral position shown in FIGS. 3 and 4, in which only the first synchronizer ring 34 is in engagement with the sliding sleeve 18, is first traversed again.

[0125] At the latest in the movement of the sliding sleeve 18 into the neutral position, only the abutment surface 39b of the locking strut 39 that faces the first synchronizer ring 34 immerses into the pre-synchronization groove, so that locking strut 39 is brought into a position tilted with respect to the axial direction.

[0126] In the further movement, the sliding sleeve 18 reaches a pre-synchronization position shown in FIG. 7, in which starting from the neutral position the locking strut is pushed toward the second synchronizer ring 40 owing to the abutment surface 39c of the sliding sleeve 18 and abutment surface 39b of the locking strut 39 coming into abutment. The locking strut 39 thereby comes into abutment against the second synchronizer ring 40 and displaces it toward the second synchronizer body 26.

[0127] In this pre-synchronization position, a first friction engagement thereby arises between second synchronizer ring 40 and the second synchronizer body 26, which in turn results in a torque on the second synchronizer ring 40. Due to this torque (in the rotational direction of the second ring gear), the second synchronizer ring 40 is brought into its lock position (relative rotation position) with respect to the sliding sleeve 18, whereby the gearings are displaced toward each other.

[0128] In the further movement of the sliding sleeve 18 into a synchronization position (see FIGS. 8 to 10), the axial ends of the gearing (chamfered teeth) of the sliding sleeve 18 impinge against the axial ends of the gearing (chamfered teeth) of the second synchronizer ring 40, whereby a higher axial force is applied onto the second synchronizer ring 40. This leads to a strengthened friction engagement, which in turn results in an increased transmission of torque (braking torque) between the second synchronizer body 26 and the second synchronizer ring 40. A further movement of the sliding sleeve 18 toward the second synchronizer body 26 is thereby blocked by the not-aligned gearings.

[0129] As is shown in FIG. 10, in the movement of the sliding sleeve 18 from its pre-synchronization position into its synchronization position, the locking strut 39 held by the spring 39a relatively rotates itself into an orientation parallel to the sliding sleeve, since the abutment surfaces 39b, 39c slip against each other. Starting from the synchronization position shown in FIG. 10, a further movement of the sliding sleeve 18 toward the second synchronizer body 26 is not obstructed.

[0130] In the synchronization position, the external gearing 36 of the first synchronizer ring 34 is still in engagement with the internal gearing 20 of the sliding sleeve 18. Between the first synchronizer ring 34 and the first synchronizer body 22, substantially no friction torque acts on the synchronizer body 22 owing to the lack of an axial force toward the first synchronizer body 22. The first synchronizer body 22 is accelerated with the braking of the second synchronizer body 26. Due to the simultaneous braking and the acceleration, a torque that arises from the torque of the synchronizer ring is still transmitted to the output shaft, i.e., to the bridge S.

[0131] As can be seen from FIG. 9, in the synchronization position the guide pin 56 is located inside the guide groove 54 slightly below the above-described neutral position.

[0132] As soon as the second synchronizer body 26 is stopped, the torque transmitted via the chamfer surfaces (axial tooth ends) of the gearings of the sliding sleeve 18 and of the second synchronizer ring 40 onto the second synchronizer ring 40 decreases (additional torque is no longer present). In the further movement of the sliding sleeve 18 toward the second synchronizer body 26, the oblique surfaces of the gearings of the sliding sleeve 18 and of the synchronizer ring 40 slip against each other, and the second synchronizer body 26 thereby aligns with the sliding sleeve 18. The internal gearing 20 of the sliding sleeve 18 substantially simultaneously comes out of engagement with the external gearing 36 of the first synchronizer ring 34.

[0133] FIGS. 11 and 12 show the end position of the sliding sleeve 18 in which the second gear is engaged (second-gear position). As also with the first-gear position, the internal gearing 20 of the sliding sleeve 18 is in engagement with the external gearing 28 of the first synchronizer body 26 over the entire width of the external gearing 28 of the first synchronizer body 26. As can be seen from FIG. 12, in the second-gear position the guide pin 56 is disposed in an opposite end position of the guide groove 54.

[0134] For the engaging of the second gear, starting from the neutral position the sliding sleeve 18 thus substantially need only travel the distance x.sub.axial,2, wherein this distance substantially corresponds to the width of the external gearing 28 of the second synchronizer body 26 plus the width of the external gearing 42 of the second synchronizer ring 40 (actually, the distance corresponds to the width of the external gearings plus the distance the internal gearing 20 has to the external gearing 42 of the second synchronizer ring 40 in the neutral position, plus the spacing between the external gearings of the second synchronizer body 26 and of the second synchronizer ring 40). In particular it is further to be noted that, at latest starting from the reaching of the synchronization position, there is a high torque on the output again, so that a load interruption occurs, if at all, only in the region of the movement through the neutral position and the pre-synchronization position, which load interruption, however, is very short due to the short time- and distance-duration of these positions and the acceleration torque of the other synchronizer body.

[0135] The above sequence occurs with a changed direction during the shifting from the second gear to the first gear. Another neutral position is first traversed, in which only the second synchronizer ring 40 is in engagement with the sliding sleeve 18. In this position, the locking strut 39 is also tilted away from the above-described position, i.e., the abutment surface 39b facing the second synchronizer body is immersed into the pre-synchronization groove. In the further movement of the sliding sleeve, a pre-synchronization position for aligning the first synchronizer ring 34 with respect to the sliding sleeve 18 in the lock position is achieved in an analogous manner (see FIG. 13). The braking of the first synchronizer body 22 subsequently occurs (not shown) in a further synchronization position for the first gear.

[0136] The width of the internal gearing 20 of the sliding sleeve 18 is preferably 10% smaller, still more preferably 5% smaller, and still more preferably 1% smaller than the distance of the external gearings 24, 28 of one of the synchronizer bodies 22, 26 to the respective opposing (associated with the respective other synchronizer body) synchronizer ring 40, 34.

[0137] A further third embodiment, which is not depicted, will be explained in the following.

[0138] Unless indicated otherwise, all features and positions of the first and second embodiment also apply to the third embodiment.

[0139] A transmission includes a housing, in which a drive shaft is supported. A sliding sleeve is supported on the drive shaft such that they rotate together, but the sliding sleeve is movable along a movement axis. The sliding sleeve has an internal gearing having a radial spacing to the drive shaft. On the drive shaft, there is provided, on the one side of the sliding sleeve, a first synchronizer body having an externally geared region, which is bringable into engagement with the internal gearing of the sliding sleeve by moving the sliding sleeve along the movement axis, and having a friction region that is formed radially inside, and is axially displaced toward the sliding sleeve with respect to the externally geared region. On the other side of the sliding sleeve, there is provided on the drive shaft a second synchronizer body having an externally geared region, which is bringable into engagement with the internal gearing of the sliding sleeve by moving the sliding sleeve along the movement axis, and having a friction region that is formed radially inside, and axially displaced toward the sliding sleeve with respect to the externally geared region. Furthermore, a first synchronizer ring is provided with an external gearing that is bringable into engagement with the internal gearing of the sliding sleeve by moving of the sliding sleeve along the movement axis, and with a friction region that is configured for support and for friction engagement on the friction region of the first synchronizer body. In an analogous manner, a second synchronizer ring is provided with an external gearing that is bringable into engagement with the internal gearing of the sliding sleeve by moving of the sliding sleeve along the movement axis, and with a friction region that is configured for support and for friction engagement on the friction region of the second synchronizer body. The transmission is thereby configured such that the sliding sleeve is bringable into a neutral position, in which the internal gearing of the sliding sleeve is not in engagement with the externally toothed regions of the synchronizer bodies, and is simultaneously in engagement with the external gearing of only one of the synchronizer rings. At the same time the sliding sleeve is configured such that, in another position, it is in engagement with the first and the second synchronizer rings simultaneously, but simultaneously not in engagement with the external gearings of the synchronizer bodies. The sliding sleeve, the synchronizer bodies, and the synchronizer rings form a locking device.

[0140] The synchronizer bodies are formed with a gear integrally or such that they rotate together; the gear has a further external gearing that is configured for meshing with gears (input- or output-shaft) on another shaft or attached thereto. By displacing the sliding sleeve (for example, using the above-described displacing device) between an engagement (a locking) with the one synchronizer body or the other synchronizer body, different gear ratios can be realized. In contrast to the first and second embodiment, in the synchronization position the gear wheels are braked or accelerated to the speed of the rotating sliding sleeve. One or more locking struts and the support of the synchronizer rings in the sliding sleeve is described as pertaining to the other embodiments.

[0141] A displacing device for displacing the sliding sleeve can be configured as in the above exemplary embodiments or in any other manner (hydraulically actuated, linear-motor actuated, etc.), in particular conventionally via shift forks.

[0142] FIG. 14 shows various shifting processes in an idealized torque- and power-characteristic-curve of an electric drive machine (E-motor), as well as the optimal efficiency range η.sub.optE-.sub.Motor of an E-motor (dependent on the type of machine, synchronous or asynchronous machine). T.sub.max indicates the nominal torque (maximum torque). T.sub.nmax indicates the maximum rotational speed torque. P.sub.max indicates the maximum power. In the embodiment described here, the shifting from the first into the second gear engages at the maximum rotational speed n.sub.max of the electric drive machine EM. Due to the very high rotational speed range with constant power (constant power range) - in comparison to combustion engines -, on the one hand a large gear step can be accepted; on the other hand it is in principle unimportant when the shifting from the first gear into the second gear is initiated, as long as the end point after the shifting into the second gear still does not exceed the maximum power range of the machine in terms of rotational speed. For the design of the friction clutch (synchronous clutch), it is recommended to perform the synchronization (the braking of the second ring gear) with the lowest-possible torque. This is the case when the E-motor is accelerated up to the maximum rotational speed n.sub.max, and only at this point (the lowest torque for the maximum power of the electric drive machine) is the shifting initiated (see point 1 in FIG. 14). The dimensioning of the friction clutch is effected normally according to torque. If the shifting is generally initiated only at the preferred rotational speed n.sub.max (as depicted), the size of the friction device is minimized and the construction is simplified. The shifting from the first gear into the second gear is then possible in two ways. If the synchronization is not regulated (if the sliding sleeve is thus moved toward the second ring gear with a constant force (by the actuator)), the torque is constant during the synchronization, and point 2 is reached. Here the dog clutch is engaged (the sliding sleeve is brought into engagement with the synchronizer body), and the torque can now be regulated by the electric drive machine in accordance with the customer demand. For this case, the synchronization torque (clutch torque) of the friction clutch is constant; in this case the actuator need not be regulated. Alternatively the clutch torque can be regulated during the shifting by the actuator such that the clutch torque corresponds to the maximum output torque of the electric drive machine for the respective rotational speed in a manner dependent on the rotational speed of the electric drive machine (curve between points 1 and 3 in FIG. 14). For this case, a constant power at the output is possible during the shifting. The same applies for a shifting in the partial-load range, which is depicted by the points 4 to 5 and 4 to 6. This is always the case when the maximum power is not demanded upon reaching the maximum rotational speed of the drive machine (this is much more often the case in normal operation). For the shifting in the partial-load range, the actuator is correspondingly controlled in a manner dependent on the power demand of the customer (the gas-pedal position), in order to reduce or to avoid a load interruption. The gear ratio of n.sub.max/n.sub.G2 corresponds to the step jump of the manual transmission. To regulate the clutch torque, an ordinary torque sensor, which is not depicted here and is not described in more detail, can be provided in the friction clutch. Alternatively the clutch torque can be controlled by empirical values, which are previously determined empirically.

[0143] Further aspects of the present disclosure:

[0144] As already indicated above, in addition to the specific application in a transmission for an electric drive system for a vehicle, the present teaching is also usable in all other shiftable transmissions having at least two speeds. The teaching is thus applicable to conventional synchronizer groups (synchronization clutch or lock-type synchronous clutches), in which a first rotating gear rotating with no rotational speed or a first rotational speed is accelerated or braked, prior to a shifting process, to a second rotational speed of a second gear (or also a shaft), and subsequently fixedly coupled to the second gear via a sliding sleeve.

[0145] In general terms the present disclosure also comprises:

[0146] Aspect 1: Shifting subassembly for a transmission, including [0147] a housing, [0148] a sliding sleeve supported in the housing to be movable along a movement axis, which sliding sleeve has an internal gearing whose central axis is provided coaxially with the movement axis, [0149] a first synchronizer body, which is disposed coaxially with the sliding sleeve, having an externally geared region that is bringable into engagement with the internal gearing of the sliding sleeve by moving the sliding sleeve along the movement axis, and having a friction region that is preferably formed radially inside, and axially toward one side toward the movement axis with respect to the externally geared region, [0150] a second synchronizer body, which is disposed coaxially with the sliding sleeve and on the side of the friction region of the first synchronizer body, having an externally geared region that is bringable into engagement with the internal gearing of the sliding sleeve by moving the sliding sleeve along the movement axis, and having a friction region that is preferably formed radially inside and axially displaced with respect to the externally geared region on the side of the first synchronizer body, [0151] a first synchronizer ring having an external gearing that is bringable into engagement with the internal gearing of the sliding sleeve by moving the sliding sleeve along the movement axis, and having a friction region that is configured for abutment against the friction region of the first synchronizer body, [0152] a second synchronizer ring having an external gearing that is bringable into engagement with the internal gearing of the sliding sleeve by moving the sliding sleeve along the movement axis, and having a friction region that is configured for abutment against the friction region of the second synchronizer body, [0153] wherein the shifting subassembly is configured such that [0154] the sliding sleeve is bringable into a neutral position, in which the internal gearing of the sliding sleeve is not in engagement with the externally geared regions of the synchronizer bodies, and is simultaneously in engagement with the external gearing of only one of the synchronizer rings.

[0155] Aspect 2: the shifting subassembly according to Aspect 1 is further configured such that, in a movement along the rotational axis, the sliding sleeve is bringable into a pre-synchronization position, in which the internal gearing of the sliding sleeve is not in engagement with the externally toothed regions of the two synchronizer bodies, simultaneously the internal gearing of the sliding sleeve is in engagement with the external gearing of only one of the synchronizer rings, and simultaneously the sliding sleeve brings a locking strut, which is provided such that it is not rotatable relative to the sliding sleeve, into axial abutment against the other of the synchronizer rings, and presses the other of the synchronizer rings against the corresponding synchronizer body, whereby the other synchronizer ring is relatively rotated with respect to the sliding sleeve into a lock position, in which the gearings of the sliding sleeve and of the other synchronizer ring are relatively rotated with respect to each other.

[0156] Aspect 3: the shifting subassembly according to Aspect 1 or 2 is further configured such that, in a movement along the rotational axis, the sliding sleeve is bringable into a synchronization position, in which the internal gearing of the sliding sleeve is not in engagement with the externally geared regions of the synchronizer bodies, and simultaneously the internal gearing of the sliding sleeve is at least partially in engagement with the external gearings of both synchronizer rings, and force is preferably exerted by the sliding sleeve onto one of the synchronizer rings in the direction of the rotational axis, so that the corresponding synchronizer body is bringable to the same rotational speed with the corresponding synchronizer ring (a torque acts on the synchronizer body) via the friction engagement.

[0157] Further aspects:

[0158] 4. Transmission for an electric drive system for a vehicle, including [0159] a housing (G), [0160] an input shaft (E) supported in the housing (G) to be rotatable about a rotational axis (X), [0161] an output shaft (A) supported in the housing (G) to be rotatable about the rotational axis (X), [0162] a first planetary transmission (10) and a second planetary transmission (12) that are disposed adjacent to each other coaxially with the rotational axis (X), and have different gear ratios with respect to each other, wherein the first planetary transmission (10) and the second planetary transmission (12) include a common planetary carrier (S) that is supported in the housing (G) to be rotatable about the rotational axis (X) and is connected to the output shaft (A), and the first planetary transmission (10) includes a first ring gear (14) supported in the housing (G) to be rotatable around the rotational axis (X), and the second planetary transmission (12) includes a second ring gear (16) supported in the housing (G) to be rotatable about the rotational axis (X), [0163] a locking device (2), using which the first ring gear (14) or the second ring gear (16) is selectively lockable to the housing (G) so that, when the first ring gear (14) is locked, a torque is transmissible from the input shaft (E) to the output shaft (A) via the first planetary transmission (10) at a first gear ratio, and when the second ring gear (16) is locked, a torque is transmissible from the input shaft (E) to the output shaft (A) via the second planetary transmission (12) at a second gear ratio, wherein [0164] the locking device (2) includes [0165] a sliding sleeve (18), which is disposed in the housing (G) such that the sliding sleeve (18) is not rotatable relative to the housing (G) and is axially movable along the rotational axis (X), and which has an internal gearing (20), [0166] a first synchronizer body (22) that is rigidly connected with the first ring gear (14) or is formed integrally therewith, and has an external gearing (24) that is configured such that it is bringable into engagement with the internal gearing (20) of the sliding sleeve (18) by moving the sliding sleeve (18) along the rotational axis (X) into a first position, and a second synchronizer body (26) that is rigidly connected with the second ring gear (16) or is formed integrally therewith, and has an external gearing (28) that is configured such that it is bringable into engagement with the internal gearing (20) of the sliding sleeve (18) by moving the sliding sleeve (18) along the rotational axis (X) into a second position, and [0167] a displacing device (46) having an actuator, using which the sliding sleeve (18) is displaceable along the rotational axis (X) between the first position and the second position.

[0168] 5. Transmission according to Aspect 4., wherein [0169] the first synchronizer body (22) has a friction region (30) on the side facing the second synchronizer body (26), and the second synchronizer body (26) has a friction region (32) on the side facing the first synchronizer body (22), [0170] a first synchronizer ring (34) is provided, which has an external gearing (36) that is configured such that it is bringable into engagement with the internal gearing (20) of the sliding sleeve (18) by moving the sliding sleeve (18), using the actuator, along the rotational axis (X), and which has a friction region (38) that is configured for abutment against the friction region (30) of the first synchronizer body (22); and a second synchronizer ring (40) is provided, which has an external gearing (42) that is configured such that it is bringable into engagement with the internal gearing (20) of the sliding sleeve (18) by moving the sliding sleeve (18), using the actuator, along the rotational axis (X), and which has a friction region (44) that is configured for abutment against the friction region (32) of the second synchronizer body (26).

[0171] 6. Transmission according to Aspect 5., wherein [0172] the locking device (2) is further configured such that, using the actuator, the sliding sleeve (18) is bringable into a neutral position, in which the internal gearing (20) of the sliding sleeve (18) is not in engagement with the external gearings (24, 28) of the synchronizer bodies (22, 26), and is simultaneously in engagement with the external gearing (36, 42) of only one of the synchronizer rings (34, 40).

[0173] 7. Transmission according to Aspect 5. or 6., wherein [0174] the locking device (2) is configured such that, using the actuator, the sliding sleeve (18) is bringable, in a movement along the rotational axis (X), into a pre-synchronization position, in which the internal gearing (20) of the sliding sleeve (18) is not in engagement with the external gearings (24, 28) of the two synchronizer bodies (22, 26), simultaneously the internal gearing (20) of the sliding sleeve (18) is in engagement with the external gearing (36, 42) of only one of the synchronizer rings (34, 40), and simultaneously the sliding sleeve (18) brings a locking strut (39), which is provided such that it is not rotatable relative to the sliding sleeve (18), into axial abutment against the other of the synchronizer rings (34, 40), and presses the other of the synchronizer rings (34, 40) against the corresponding synchronizer body, whereby the other synchronizer ring is relatively rotated with respect to the sliding sleeve into a lock position, in which the gearings (20) of the sliding sleeve (18) and of the other synchronizer ring are relatively rotated with respect to each other.

[0175] 8. Transmission according to one of Aspects 5. to 7., wherein [0176] the locking device is configured such that, using the actuator, in a movement along the rotational axis (X), the sliding sleeve (18) is bringable into a synchronization position, in which the internal gearing (20) of the sliding sleeve (18) is not in engagement with the external gearings (24, 28) of the two synchronizer bodies (22, 26), and simultaneously the internal gearing (20) of the sliding sleeve (18) is at least partially in engagement with the external gearings (36, 42) of both synchronizer rings, and force is preferably exerted by the sliding sleeve (18) in the direction of rotation (X) onto one of the synchronizer rings (34, 40) such that the corresponding synchronizer body (22, 26) is brakeable by the friction engagement with the one synchronizer ring (34, 40).

[0177] 9. Transmission according to one of Aspects 5. to 8., wherein [0178] the locking device is configured such that the torque transmission via the first planetary transmission (10) is realized by bringing the sliding sleeve along the rotational axis (X) using the actuator into a first-gear position, in which the internal gearing (20) of the sliding sleeve (18) is in engagement with the external gearing (24) of the first synchronizer body (22), and is simultaneously not in engagement with the external gearings (28, 42) of the second synchronizer body (26) and of the second synchronizer ring (40), and such that the torque transmission via the second planetary transmission (12) is realized by bringing the sliding sleeve (18) along the rotational axis (X) using the actuator into a second-gear position, in which the internal gearing (20) of the sliding sleeve (18) is in engagement with the external gearing (28) of the second synchronizer body (26), and simultaneously is not in engagement with the external gearings (24, 36) of the first synchronizer body (22) and of the first synchronizer ring (34).

[0179] 10. Transmission according to one of Aspects 5. to 9., wherein [0180] the width of the internal gearing (20) of the sliding sleeve (18) in the direction of the rotational axis (X) is greater than the spacing of the external gearings (36, 42) of the synchronizer rings (34, 40) in the direction of the rotational axis (X) and is smaller than the distance of the external gearing (24, 28) of one of the synchronizer bodies (22, 26) to the external gearing of the respective other synchronizer ring (40, 34) in the direction of the rotational axis (X).

[0181] 11. Transmission according to one of Aspects 4. to 10., wherein [0182] the diameter of the internal gearing (20) of the sliding sleeve (18) is greater than the diameter of the internal gearing of the smaller ring gear (14, 16).

[0183] 12. Transmission according to one of Aspects 4. to 11., wherein [0184] the first planetary transmission (10) includes a first sun gear (1′), which is provided on the input shaft (E) such that they rotate together, and a first planetary gear (6′), which is rotatably supported on the planet carrier (S) and meshes with the first sun gear (1′) and with the first ring gear (14), and [0185] the second planetary transmission (12) includes a second sun gear (1), which is provided on the input shaft (E) such that they rotate together, and a second planetary gear (6), which is rotatably supported on the planet carrier (S) and meshes with the second sun gear (1) and with the second ring gear (16).

[0186] 13. Transmission according to one of Aspects 4. to 12., wherein [0187] the first planetary transmission (10) includes a first planetary gear (6′), which is rotatably supported on the planet carrier (S) and meshes with the first ring gear (14), and the second planetary transmission (12) includes a second planetary gear (6), which is rotatably supported on the planet carrier (S) and meshes with the second ring gear (16), [0188] the first planetary gear (6′) and the second planetary gear (6) are fixedly connected to each other, [0189] the first or the second planetary gear (6′, 6) meshes with a sun gear (1), which is provided on the input shaft (E) such that the sun gear (1) and the input shaft (E) rotate together, and [0190] preferably the two planetary gears, which are fixedly connected to each other, are configured as step planetary gears, of which only one step meshes with the sun gear (1).

[0191] 14. Transmission according to one of aspects 4. to 13., wherein [0192] the displacing device (46) includes, [0193] a worm shaft (50) that is drivable by the actuator (48), and [0194] a worm gear (52) that is disposed coaxially with the sliding sleeve (18) and is disposed on the outer circumference side with respect thereto such that, as viewed starting from the rotational axis (X) in a radial direction perpendicular to the rotational axis (X), the sliding sleeve (18) at least partially overlaps the worm gear (52) and is rotatable by the worm shaft (50) around the rotational axis (X), and [0195] a guide pin (56) that is provided on the sliding sleeve (18) and protrudes radially outward therefrom, wherein [0196] a guide groove (54) for receiving the guide pin (56) is provided in the worm gear (52), the guide groove (56) extending at an angle (α) to the circumferential direction so that, during the rotation of the worm gear (52) by the angle (β), a displacement of the sliding sleeve (18) along a distance (x) occurs, and [0197] the actuator is configured as an electric motor.

[0198] 15. Transmission according to one of Aspects 4. to 14., wherein [0199] the sliding sleeve (18) has an external gearing on its outer side, using which external gearing it is guidable along the rotational axis (X) in an internal gearing in the housing (G).

[0200] 16. Transmission according to one of Aspects 4. to 15., wherein [0201] the ring gears (14, 16) are supported radially on the planetary gears (6′, 6), and bearings are respectively disposed for axial support between the ring gears and between their sides facing away from each other and the housing.

[0202] 17. Transmission according to one of aspects 4. to 16., wherein [0203] the input shaft (E) is supported in the planet carrier (S) via a bearing, or [0204] the planet carrier (S) is supported on the input shaft (E).

[0205] 18. Transmission, including [0206] a housing (G), and [0207] a locking device (2), wherein [0208] the locking device (2) includeswherein the locking device is configured such that [0209] a sliding sleeve (18), which is supported in the housing to be movable along a movement axis, having an internal gearing (20) whose central axis is provided coaxially with the movement axis, [0210] a first synchronizer body (22), which is disposed coaxially with the sliding sleeve (18), having an external gearing (24), which is bringable into engagement with the internal gearing (20) of the sliding sleeve (18) by moving the sliding sleeve (18) along the movement axis, and having a friction region (30), which is preferably formed radially inside, and axially toward one side toward the movement axis with respect to the external gearing (24) of the first synchronizer body (22), [0211] a second synchronizer body (26), which is disposed coaxially with the sliding sleeve (18) and on the side of the friction region (30) of the first synchronizer body (22), having an external gearing (28), which is bringable into engagement with the [0212] internal gearing (20) by moving the sliding sleeve (18) along the movement axis, and having a friction region (32), which is preferably formed radially inside and axially displaced with respect to the external gearing (28) of the second synchronizer body (26) on the side of the first synchronizer body (22), [0213] a first synchronizer ring (34) having an external gearing (36), which is bringable into engagement with the internal gearing (20) of the sliding sleeve (18) by moving the sliding sleeve (18) along the movement axis, and having a friction region (38), which is configured for abutment against the friction region (30) of the first synchronizer body (22), and [0214] a second synchronizer ring (40) having an external gearing (42), which is bringable into engagement with the internal gearing (20) of the sliding sleeve (18) by moving the sliding sleeve (18) along the movement axis, and having a friction region (44), which is configured for abutment against the friction region (32) of the second synchronizer body (26), [0215] the sliding sleeve (18) is bringable into a neutral position, in which the internal gearing (20) of the sliding sleeve is not in engagement with the external gearing (24) of the first synchronizer body (22), and is not in engagement with the external gearing (28) of the second synchronizer body (26), and is simultaneously in engagement with the external gearing (36, 42) of only one of the synchronizer rings (34, 40).

[0216] 19. Transmission according to Aspect 18., which is further configured such that [0217] in a movement along the rotational axis (X), the sliding sleeve (18) is bringable into a pre-synchronization position, in which the internal gearing (20) of the sliding sleeve (18) is not in engagement with the external gearings (24, 28) of the two synchronizer bodies (22, 26), simultaneously the internal gearing (20) of the sliding sleeve (18) is in engagement with the external gearing (36, 42) of only one of the synchronizer rings (34, 40), and simultaneously the sliding sleeve (18) brings a locking strut (39), which is provided such that it is not rotatable relative to the sliding sleeve (18), into axial abutment against the other of the synchronizer rings (34, 40), and presses the other of the synchronizer rings (34, 40) against the corresponding synchronizer body, whereby the other synchronizer ring is relatively rotated with respect to the sliding sleeve (18) into a lock position, in which the gearings of the sliding sleeve (18) and of the other synchronizer ring are relatively rotated with respect to each other, and/or [0218] in a movement along the rotational axis (X), the sliding sleeve (18) is bringable into a synchronization position, in which the internal gearing (20) of the sliding sleeve (18) is not in engagement with the external gearings (24, 28) of the two synchronizer bodies (22, 26), and simultaneously the internal gearing (20) of the sliding sleeve (18) is at least partially in engagement with the external gearings (36, 42) of both synchronizer rings, and preferably force is exerted by the sliding sleeve (18) onto one of the synchronizer rings (34, 40) in the direction of the rotational axis (X), so that the corresponding synchronizer body (22, 26) is synchronizable with the one synchronizer ring (34, 40) via the friction engagement.

[0219] 20. Transmission according to Aspect 18. or 19., which is further developed with the characterizing features of at least one of Aspects 7., 8., and 12.

[0220] 21. Transmission according to one of Aspects 18. to 20., which further includes [0221] a displacing device (46) having an actuator, using which the sliding sleeve (18) is displaceable along the rotational axis (X).

[0222] 22. Transmission according to one of Aspects 18. to 21., which further includes [0223] an input shaft (E) supported in the housing (G) to be rotatable about a rotational axis (X), [0224] an output shaft (A) supported in the housing (G) to be rotatable about the rotational axis (X), [0225] a first planetary transmission (10) and a second planetary transmission (12), which are disposed adjacent to each other coaxially with the rotational axis (X), and have different gear ratios with respect to each other, wherein the first planetary transmission (10) and the second planetary transmission (12) include a common planetary carrier (S), which is supported in the housing (G) to be rotatable about the rotational axis (X) and is connected to the output shaft (A), and the first planetary transmission (10) includes a first ring gear (14), which is supported in the housing (G) to be rotatable around the rotational axis (X), and the second planetary transmission (12) includes a second ring gear (16), which is supported in the housing (G) to be rotatable about the rotational axis (X), wherein [0226] using the locking device (2), the first ring gear (14) or the second ring gear (16) is selectively lockable to the housing (G) so that, when the first ring gear (14) is locked, a torque is transmissible from the input shaft (E) to the output shaft (A) via the first planetary transmission (10) at a first gear ratio and, when the second ring gear (16) is locked, a torque is transmissible from the input shaft (E) to the output shaft (A) via the second planetary transmission (12) at a second gear ratio.

[0227] 23. Transmission according to Aspect 22., as dependent on Aspect 21., which is further developed with the characterizing features of at least one of Aspects 9. and 12., 13., 14., 16., and 17.

[0228] It is self-evident that a transmission having such a shifting subassembly is also encompassed by the teaching.

[0229] The appended dependent claims are freely combinable with above Aspects, wherein the term “locking device” is to be equated with “shifting subassembly,” and the term “external gearing of the synchronizer bodies” is to be equated with “externally geared regions of the synchronizer bodies.”

[0230] It is explicitly emphasized that all of the features disclosed in the description and/or the claims should be considered as separate and independent from one another for the purpose of the original disclosure as well as for the purpose of limiting the claimed invention, independent of the combinations of features in the embodiments and/or the claims. It is explicitly stated that all range specifications or specifications of groups of units disclose every possible intermediate value or subgroup of units for the purpose of the original disclosure as well as for the purpose of limiting the claimed invention, in particular also as the limit of a range specification.

[0231] The Figures are to be regarded as purely schematic. Figures, which are to show different states and views of the same embodiment, can also represent details of the embodiment in different degrees of detail. The functional and structural description remains relevant.

[0232] The terms “roughly,” “about,” “approximately,” “substantially,” or “generally” used here, which are used in connection with a measurable value such as, for example, a parameter, a quantity, a shape, a time duration, or the like, include deviations or fluctuations of ± 10% or less, preferably ± 5% or less, further preferably ± 1% or less, and further preferably ± 0.1% of the respective value or from the respective value, provided these deviations are still technically useful in practice in the implementation of the disclosed invention. Ultimately the longitudinal or dimensional tolerances of the component determine the deviations or fluctuations of the parameters. It is expressly indicated that the value to which the term “approximately” refers is explicitly and specifically disclosed as such. The indication of ranges by initial and final values comprises all those values and fractions of those values that are enclosed by the respective range as well as its initial and final values.

TABLE-US-00001 Reference Number List EM Electric drive machine (E-motor) E Input shaft A Output shaft X Rotational axis G Housing S Bridge α Angle of inclination of the groove in the worm gear β Circumferential angle (“length”) of the groove 1′ First sun gear 1 Second sun gear 2 Locking device 6′ First planetary gear 6 Second planetary gear 10 First planetary transmission 12 Second planetary transmission 14 First ring gear 16 Second ring gear 17 Stepped connecting component 18 Sliding sleeve 20 Internal gearing of the sliding sleeve 22 First synchronizer body 24 External gearing of the first synchronizer body 26 Second synchronizer body 28 External gearing of the second synchronizer body 30 Friction region of the first synchronizer body 32 Friction region of the second synchronizer body 34 First synchronizer ring 36 External gearing of the first synchronizer ring 38 Friction region of the first synchronizer ring 39 Locking strut 39a Spring 39b Abutment surface of the locking strut 39c Abutment surface of the sliding sleeve 40 Second synchronizer ring 42 External gearing of the second synchronizer ring 44 Friction region of the second synchronizer ring 46 Displacing device 48 Electric motor 50 Worm shaft 52 Worm gear 54 Guide groove in the worm gear 56 Guide pin in the sliding sleeve 58 First bearing for the stepped planets 60 Second bearing for the stepped planets 62 Axial bearing between the ring gears

TWO-SPEED TRANSMISSION FOR AN ELECTRIC DRIVE SYSTEM, AND DRIVE SYSTEM INCLUDING SUCH A TWO-SPEED TRANSMISSION

Inventors

Cpc classification

Classification Explorer

F16H2200/2041

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16D11/04

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2063/3066

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2200/2005

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16D2023/123

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16D28/00

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2200/2094

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16D23/04

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2200/2064

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2200/0021

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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B60Y2200/91

PERFORMING OPERATIONS; TRANSPORTING

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F16D21/04

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2057/02043

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2063/3056

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2057/02034

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2200/2007

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2061/0418

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H3/663

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H61/0403

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2200/0034

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H3/66

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H3/78

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H63/304

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16D23/025

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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F16H2200/2035

MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

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